Lower effort quick-disconnect coupler

ABSTRACT

This invention relates to an improvement in the manner by which the direct response sealing member (valve) is opened or uncoupled by substantially reducing the required insertion force and hence reducing the work required. A fluid channel opening of the direct response valve is initiated by the insertion of a typical male quick-disconnect coupling into a typical female quick-disconnect coupling containing this new direct response valve. A new direct response valve is designed to ensure that the internal sealing member is firstly opened in a rotational manner and then secondly, if desired, in a more typical translational manner. The new sealing member is designed to be backward compatible with existing two part quick-disconnect assemblies and this facilitates a simple one part substitution to benefit from this improvement.

BACKGROUND OF THE INVENTION

This invention involves a direct response valve with a sealing membercomponent that is opened by a manner of rotation of the sealing memberand then, if desired, continues to open by axial translation of thesealing member. The design functionality utilizes othercommercially-available standard components; where some, although notall, components are necessary for the new design to function. Inparticular, two components from pre-existing commercially availabledesigns are utilized here in order to ensure that the new directresponse valve can function and are part of this system: 1) radial“seal” between the male and female coupler and, 2) “stop and lock” or“lock” which locks the male and female coupler together under fullengagement of the quick-disconnect connector.

Quick-disconnect couplers are in widespread use for reliably joiningfluid transfer lines, gas transfer lines and pneumatic transfer lines.Generally, an automatic shut-off value is provided, commonly called adirect response valve, which incorporates an integral valve (directresponse valve with a sealing member) to seal the central passageway ofthe coupler automatically upon uncoupling. This integral direct responsevalve eliminates the need for a separate shut-off valve that would haveto be actuated prior to the uncoupling; the purpose of a shut-off directresponse valve is to eliminate undesirable leakage. In general,quick-disconnect couplers use many variations of locking mechanisms toautomatically lock the two components of the quick coupling mechanism sothat the user does not have to manually hold the two parts of thecoupler together while fluid flow, thus supporting practicability. Themethods of locking are varied and numerable. The type of lockingfeatures of a typical quick-disconnect coupler is not of materialrelevance to this discussion due to the fact that any manner of lockingis merely to provide practical convenience to the user.

In addition, all direct response valves contain a central sealing memberwhich is typically located in the female coupling assembly and thiscomponent can take many different shapes. The primary features of thedesign of the valve are: 1) that it must comprise a smaller size thanthe inside annular cavity of the female coupling body and, 2) that thesealing members axial sealing surface must closely match in acircumferential manner the same or similar axial shape of surfaces asthe matching female coupling. This seal takes many forms and shapes andmaterials and can be manufactured from a separate and pliable rubbermaterial or a hard material; although in practice, the seal is typicallymuch more deformable than the parent female and male bodies, in order toensure that sealing occurs.

In addition, a radial seal is required that creates a seal between theouter portion of the male coupling and the inner diameter of the femalebody to prevent fluid communication out of the assembly, which iscommonly referred to as a “leak”. Also this radial seal ensures that thequick-disconnect connector functions and hence fluid flows between thefemale and the male coupler only and does not “leak” out of the coupler.

In the past, a number of quick-disconnect couplings utilize a directresponse valve, whereby the sealing member is caused to open by theinsertion of a male coupler and the resultant axial movement of thesealing member. Typically the forward surface of the male coupler (whichis of uniform length in the axial direction) communicates with theraised surface of the sealing member of the direct response valvemember, thus causing all parts of the sealing member to translate in apure axially uniform manner. Hence the sealing member and the malecoupler axial movement coincide in their direction and deflectionamount.

Prior-art direct response valves, also known as check valves, aredisclosed in Applicant's previous U.S. Pat. Nos. 8,561,640 B2;5,005,602; 4,712,575; 4,776,369; 7,334,603; 6,978,800 and 8,596,560 B2.These prior-art disclosures incorporate only a purely axially movementof the sealing member, relative to the direct response valve body(female body and/or male body), which provided a movement where all ofthe sealing surfaces moved the same amount, providing a uniformcircumferential opening at all locations between the sealing surfaces.Since the sealing member is translating purely axially, against theresisting fluid pressure, this means that the resulting force (ofinsertion of the connector) will have to overcome all the resistingpressure contained within the central chambers of the female body. Thepresent invention is unique in that it is designed to ensure that theinternal sealing member is firstly opened in a rotational manner andthen secondly, if desired, in a more typical axial translational manner.This invention provides distinctive human functional advantages, due tothe rotation of the sealing member during opening, namely lowering theeffort of insertion as compared to prior-art submissions.

Prior-art check valves (direct response valves) are disclosed inApplicant's previous U.S. Pat. Nos. 6,622,205; 5,941,278; 7,533,693 and5,117,514 which incorporate only pure rotational means of opening avalve (or check valve) and which utilize a sealing member and a fixedrotational movement with a mechanical pivot hence whose elements aredistinctly different than this submission. In addition they are not pureinline direct response (check) valves, as this submission, although theymay be used as a check valves in their engaged positions.

Prior-art valves are disclosed in Applicant's previous U.S. Pat. Nos.5,501,427 (251/228); 5,620,015 and 4,561,630 and all provide bothsealing member physical rotation and sealing member physicaltranslational aspects in their designs. Although all these prior-artsubmissions incorporate dramatically different mechanism design elementsin order to facilitate these sealing members rotational and axialmovements. All prior-art submissions incorporate various combinations ofthe following elements, in order to create the rotation and translationof their sealing member/s, including complex mechanisms, pivots, levels,cams, sliding, wheels, counter-balance, movably connected, pressuretrips, lost motion, slides, latches and limit stops. The previoussubmissions are dramatically different than the current submission asthey involve some of the above stated elements to facilitate rotationand translation. In addition Applicant U.S. Pat. No. 5,620,015 isspecially designed for use as a pipe end valve only and is notconsidered a pure direct response valve due to the mechanisms utilizedin its design. Applicant U.S. Pat. No. 5,501,427 is specificallyintended as a shut-off and flow regulation valve and is not a directresponse in its dis-engaged position. Lastly, Applicant U.S. Pat. No.4,561,630 is specifically intended as an extended period shut-off valveand is not a direct response valve in its dis-engaged position.

Prior-art valves are disclosed in Applicant's previous U.S. Pat. No.8,348,661 which incorporates true rotation of the sealing member aboutits longitudinal shaft axis only and no rotation of the sealing memberoccurs, as does in this submission.

BRIEF SUMMARY OF THE INVENTION

This invention relates to an improvement in the manner in which thedirect response valve member is opened or uncoupled by substantiallyreducing the required insertion force (during simple insertion) andhence reducing the work of insertion. This is accomplished by ensuringthat fluid communication can occur between the two couplings (male andfemale couplings) or the two quick-disconnect couplings, so as tosubstantially improve the ease of the insertion of the coupling.

This new direct response valve includes features which ensure that thesealing member is firstly movably opened in a rotational manner, thensecondly in a more typical axial manner. A fluid channel opening of thedirect response valve is initiated by the insertion of a typical malequick-disconnect coupling into the female quick-disconnect coupling.This female quick-disconnect coupling contains a typical direct responsevalve (sealing member) which incorporates features that ensure thesealing member initially opens in a rotational manner. At the outset, anaxial seal exists between the sealing member and the female body. Theinitial fluid channel opening between the female body of thequick-disconnect valve and typical direct response valve first occurs ata singular circumferential location which initiates fluid communicationbetween the central chambers of the male and female couplings. As themale coupling is inserted further, the fluid opening extends past asingular circumferential location and the direct response valve sealingmember continues to rotate further as the male coupling is inserted.Lastly, the sealing member is translated in an axial direction, althoughthe structure remains rotated to further open and improve fluidcommunication. If desired, the male and female coupling can be, ifdesired, held together in the final position by the use of anycommercially existing locking mechanisms. The seal between the directresponse valve and the female coupling can also be provided bycommercially existing means such as flexible materials, ‘o’ rings,precision machining or any other desired methods.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a block view in partial section of an existing typicalquick-disconnect incorporating: typical male and typical femalecouplers, a typical integrated direct response valve and typical fluidtransmission hoses (tubes, pipes). This is a block diagram of thetypical existing design which is included for comparison purposes. Thevalve is depicted in its closed position.

FIG. 2 is an external orthographic block view of a typicalquick-disconnect coupling as in FIG. 1 which details the typical blocksections. This block external view of a typical quick-disconnectcoupling also shares the typical hoses (tubes, pipes). Both the existingdesigns and the new design of block quick-disconnect couplings looksimilar from an external perspective. FIGS. 1 and 2 are included forcomparison purposes.

FIG. 3 is a half-section blow-up view taken along line 1-1 of FIG. 2.This is a detailed diagram of an existing typical quick-disconnectdesign which is provided for comparison purposes only.

FIGS. 4A, 4B and 4C are the plan and side views of three of manypossible physical methods to design the sealing members protrudingsurfaces. These three examples each incorporate an angled surface of thesealing member which is a primary feature of this new design.

FIGS. 5A, 5B and 5C are multiple side views of various possible shapesof the individual distinct protruding members highlighting the member'seffective heights. These examples of possible geometries of protrudingmembers are provided to demonstrate the principle of the effectiveheights of individual protruding members as used in the two possibledesigns shown in FIGS. 4A and 4C.

FIG. 6 is an exploded view in section taken along line 4-4 of FIG. 9,incorporating one of a chosen sealing member as detailed in FIG. 4B. InFIG. 6, the sealing member is orientated in the position prior to anymovement of the sealing member. The sealing member design of FIG. 4B ischosen only for simplification and ease of explanation since itsgeometry (cylindrical shape) is the most easily displayed.

FIG. 7 is a cross sectional view taken along line 7-7 of FIG. 6. Thepurpose of this figure is to depict sealing surfaces in plan view. Thesealing member is removed from this diagram to provide clarity.

FIGS. 8A, 8B and 8C are sectional views along line 7-7 (similar to FIG.6) showing the male coupler at different stages of engagement. FIG. 8Ais a depiction of the new quick-disconnect coupler in its first contactstage; at this stage the valve is in its closed position. FIG. 8B is adepiction of the new quick-disconnect coupler in full contact aftercomplete rotation of the sealing member; at this stage the valve is inits initially-opened position. FIG. 8C is a depiction of the newquick-disconnect coupler in the final fully engaged stage; at this stagethe valve is in its fully-opened position.

FIG. 9 is an external orthographic block view of the newquick-disconnect coupling which is detailed in FIGS. 6, 8A, 8B and 8C.This is a block external view of the new existing design with thetypical hoses (tubes, pipes). Both the existing design and the newdesign of block quick-disconnect couplings look similar from an externalperspective.

DETAILED DESCRIPTION OF DRAWINGS

FIG. 1 is a block view in partial section of a typical quick-disconnectcoupling a typical existing connector allowing fluid communication thatincorporates an integrated direct response valve with a sealing member.The position and the style or type of the exact sealing member shown isinsignificant and FIG. 1 is simply displayed for comparison purposesonly. FIG. 1 does not show or represent the required elements of theinvention claimed; rather it is included as a block diagramrepresentation which will provide a basis and framework for moredetailed elaboration. FIG. 1 also outlines the interfaces betweentypically utilized fluid transmission hoses (tubes, pipes) that areconnected to both ends of the exiting typical quick-disconnectassemblies. The direct response valve is depicted in its closedposition.

FIG. 2 is another block view section of a typical quick-disconnectcoupling (as in FIG. 1) but is represented here-in although in pictorial(orthographic) view in order to further detail sectional views and blockcomponents.

FIG. 3 is a sectional view taken along line 1-1 of FIG. 2. For ease ofdisplay, an existing typical direct response valve is shown here so thatcommon surfaces can be easily shown. The sectional views shown in FIG. 3also do not incorporate the new required details of the invention thatwe are making claim to since FIG. 3 details existing designs. FIG. 3does contain other components of a typical direct response valve,therefore proving the basis (starting point) upon which modifications tothe typical sealing member of the direct response valve are imposed forthe invention described heir-in. The direct response valve is depictedin its closed position.

A typical existing direct response valve has surface 214 and surface 216in the same plane as each other—in parallel planes. In other words thereis no intentional, or substantial, angle between surface 214 and surface216 by design or in practice. However there may be a small unintentionalangle that exists between surface 214 and surface 216 due tomanufacturing deviations and tolerances of manufactured parts. In atypical existing response valve the male coupler 203 moves in direction910 where the male coupler 203 contacts sealing member 210 at surfaces217 and 216, respectively. This after mentioned description assumes thatpart 204 is stationary although the reverse of this movement is alsopossible; where part 204 moves in direction 905 and 203 is stationary.The resultant movement, described above in direction 910 or direction905, both result in surface 214 and surface 215 no longer being incontact with each other and hence the fluid seal is broken. Thisresultant seal break (between surface 214 and surface 215) results in acommunication of fluid between internal central chambers 580 and 570.This communication of fluid continues to improve as the physical openingbetween surface 215 and surface 214 are moved relatively further apartas the quick-disconnect connector is further engaged by independentmovement in direction 910 or direction 905. In the existing typicaldesigns, since there is no angle between surfaces 214 and 216 (onparallel planes), the typical response valve (sealing member) 210 movesonly in a linear manner in direction 910 or direction 905, thereforethere is no intentional or meaningful rotation of 210 relative to 203 or204 (or axis 100) during the opening process. Since there is no rotationin the typical design, the force required to move 210 against theinternal pressure in central chamber 580 (which typically exists due tothe contained pressurized fluid) can be calculated as follows: quotientof the size of the area (surface 590 in compatible area units)multiplied by the internal pressure (in compatible pressure units) thatexists in central chamber 580. The pressure in central chamber 570 isassumed to be a low value approaching atmospheric pressure and istherefore considered negligible.

DETAILED DESCRIPTION OF THE INVENTION

A direct response valve is designed to ensure that the internal sealingmember is firstly opened in a rotational manner and then secondly, ifdesired, in a more typical axial translational manner. Following theinitial rotational phase, the sealing member is now translated in anaxial direction (although remains rotated) which further opens flowchannels, improving fluid communication.

FIGS. 4A, 4B and 4C are three examples of different designs of sealingmember's protrusions that would serve to ensure that the contactsurfaces define a distinct and intentional angle between the sealingmember's contact surfaces and the sealing surfaces. The design of thisdistinct and intentional angle ensures that the sealing member firstlyrotates during the valve opening sequence.

Note that this paragraph is identical to the previous paragraph althoughthe details of various possible designs have been added in brackets.FIGS. 4A through 4C are three examples of different designs of sealingmember's protrusions (protrusions are: groups 270 thru 273, a singular288, and groups 274 thru 276, respectively) that would serve to ensurethat the contact surfaces (contact surfaces are: surface 292, surface277 and surface 291, respectively) define a distinct and intentionalangle between sealing members contact surfaces (contact surfaces are:surface 292, surface 277 and surface 291, respectively) and the sealingsurfaces (sealing surfaces are: surface 279, surface 278 and surface285, respectively). This distinct and intentional angle (Theta1, Theta2and Theta3), by design, ensures that the sealing member firstly rotatesduring the valve opening sequence.

FIGS. 4A, 4B and 4C are three examples of sealing members that ensurethis rotation occurs by design and are detailed below. There are alsoother designs of protrusions (a feature of the sealing member; see FIGS.5A, 5B and 5C) that would ensure this desired initial rotation occursfollowed by linear translation (if desired) along axis 100. As depictedin FIG. 8, if sufficient area is exposed by rotation to separate surface330 and surface 278, allowing for sufficient fluid or gas flow, then thesecond purely linear translation (along axis 100) may be not required.Please note that the secondary linear translation of the sealing memberis also unique in that the sealing member 288 is already rotated (unliketypical sealing members) and is then translated linearly in a rotatedposition along axis 100.

FIG. 4A is the plan and side view of a possible design of the inventionthat depicts one physical method of designing the sealing member's part261. This potential design incorporates four distinct and separateprotrusions, namely 270, 271, 272 and 273. The four collective ends offour protruding surfaces (a system) define a flat plane, or the surface292. This surface 292 is at a distinct angle Theta1 relative to surface279. A design may also incorporate less than four protruding surfaces asshown in FIG. 4C whereby three surfaces are utilized. Also, more thanfour protruding surfaces may be incorporated into the design, althoughno design considerations above three or four protruding surfaces provideany practical advantages since a surface can be uniquely defined by thelocation of three points in space.

FIG. 4B is the plan and side view of another design that represents oneother physical method to design sealing member 288. This design, asdetailed in FIG. 4B, does not have distinct and separable protrusions asdo the designs shown in FIGS. 4A and 4C. The design of sealing member288 incorporates a singular protruding cylindrical shape with interiorsurface 306 and exterior surface 308 with the cylindrical shape beingattached at one end to surface 278.

As depicted in FIG. 4B, this second design of sealing member 288 alsoincorporates a number of round shaped holes 260, although the shape ofthe holes is not restricted to round-shaped holes only. Holes 260 of anyshape can be utilized as long as the resultant total area of all holesis sufficient to allow desired fluid flow quantities. The holes 260 arerequired since the shape is cylindrical (unlike the other two designs inFIGS. 4A and 4C). By its nature, this cylindrical shape would preventfluid flow without any type of holes. The interior surface 306 of theprotruding cylinder is defined by the interior diameter 224 and theouter surface 308 is defined by the exterior diameter 223. Thisprotruding cylinder (diameter 223 and 224) may also take an irregular ornon-cylindrical shape, although it must also incorporate the required260 holes and the alternative shape must also not interfere as describedwithin this paragraph. The surface 308 must not interfere duringoperation with the interior surface 305, as the sealing member rotatesand/or translates during operation. Similarly, surface 304 must notinterfere with the cavity's interior diameter 560 as defined by surface301, as the sealing member rotates and/or translates during operation.These interference requirements are also applicable for all designsdepicted by FIG. 4A and FIG. 4C where the external radial surfaces ofthe protrusions (as a system) are the elements which must not interferewith surface 305.

FIG. 4C is the plan and side view of yet another design (thirdpossibility) that represents one physical method to design sealingmember's 262 protruding surfaces. The protruding surfaces, which arerequired in this design, incorporate three distinct and separateprotrusions, specifically 274, 275 and 276. The three collective ends ofthese protruding members (which form a system) define a flat plane 291(or surface 291). This surface 291 is at a distinct angle Theta3relative to surface 285.

In concept, an alternative design could also incorporate only twoprotruding surfaces, located circumferentially about 180 degrees fromeach other (around axis 100) to provide a high point (similar to 251 bof design in FIG. 4B) and a low point (similar to 250 b of design inFIG. 4B); however this design may be unstable in practice, because thefluid and/or gas flow may rock or pulsate the sealing member thus makingthe physical design unstable. This design does incorporate the threerequired points needed to define a plane, although two of these pointsare located on the same protruding member (since these two points are invery close proximity to each other) which results in a poor (unstable orunreliable) physical plane definition.

A general statement which relates to all designs (refers to all designsdiscussed heir in and all other designs which meet the intention of thisapplication) is made in the following paragraph. This general statementwill be described using the design as depicted in FIG. 4B for ease ofexplanation, within the corresponding figure labels included in squarebrackets for the other two possible designs. Format is as follows: “FIG.4B labels [FIG. 4A labels; FIG. 4C labels]”.

Surface 282 [290; 286] can be parallel to plane 278 [279; 285] which istypically the case the practical design for manufacturingconsiderations. This new design does not define or rely on these twosurfaces (i.e. 282 [290; 286] and 278 [279; 285]) being on parallelplanes. In fact, surface 282 [290; 286] can take any physicallypractical shape required within the following stated limitations. Bothsurfaces 304 [280; 294] and surface 282 [290; 286] must not interferewith interior surface 301 as the sealing member 288 [261; 262] rotatesand translates in operation. Surface 308 [exterior outermost radialsurfaces of protrusions 270 thru 273; exterior outermost radial surfacesof protrusions 274 through 276] must not interfere with interior surface305 as the sealing member 288 [261; 262] rotates and/or translates inoperation. Either exterior surface 308 [external outermost surfaces ofprotrusions 270 thru 273; external outermost surfaces of protrusions 274thru 276] or exterior surface 304 [280; 294] can serve to centre(interfere) sealing member 288 [261; 262] against surfaces 305 [305;305] and 301 [301; 301] of part 401, respectively. In addition thesurfaces or seals present between surface 278 [279; 285] and matingsurface 330 [330; 330] can also incorporate physical characteristicsthat centre part 288 [261; 262] in its desired location relative to theaxis 100. However, any form of centering action (interference) cannotimpede the desired rotation and translation of 288 [261; 262] duringoperation as described earlier.

The detailed design of the seal between surface 278 [surface 279;surface 330 ] and surface 330 [330; 330] of FIG. 6 are not consideredpart of this invention, and as such are shown in a non-detailed andpictorial fashion only; they must simply seal by any manner desired. Theseal between surface 278 and surface 330 could be provided by one of anystandard “o” ring design or flat pliable seal design or simply a sealwhich relies on conforming materials or precision machining or othermethods.

The functioning designs must incorporate one high point (as in example251 b [251 a; 251 c]) and one low point (as in example 250 b [250 a; 250c]) which in turn defines Theta2 [Theta1; Theta3] angle as depicted inFIG. 4B [FIG. 4A; FIG. 4C]. The location circumferential of the high andlow point relative to the body 401 and 400 is not critical, although thehigh and low points should be located approximately 180 degrees fromeach other (approximately across from each other though axis 100). Thisis to ensure a rotating motion and creation of an angle Theta2 [Theta1;Theta3]. Although, in theory, there could be more than one high point(as in example 251 b [251 a; 251 c]) and more than one low point (as inexample 250 b [250 a; 250 c]) some of these additional points may beredundant (no contact) and redundant points will not improve thefunction of rotating 288 [261; 262]. Of less significant importance isthat these additional high and low points (more than one point) may alsohamper the consistent and predictable rotation of 288 [261; 262].

FIG. 5A is the side view of one possible shape of the individual anddistinct protruding members which may be incorporated into this design.Examples with distinct protruding members are shown in FIGS. 4A and 4Cin order to demonstrate that the protruding members can take variousshapes, with one possibility being 254 as shown in FIG. 5A. FIG. 5A alsoshows the effective height of this protruding member 254 as being height(or length) 253. One end of protruding members 254 is solidly connectedto and is an integral part of the base 214. Surfaces 279 and 285 (FIGS.4A and 4C, respectively) in the detailed designs of sealing members arein fact the same surface of the common base surface 214 as shown inFIGS. 5A, 5B and 5C. FIG. 5B is another possible shape of the protrudingmember as is FIG. 5C. These three examples (FIGS. 5A, 5B and 5C)indicate that the effective heights 253 of all three protruding membersare shown as having the same height regardless of their shape orapparent top surface details. This demonstrates that the effectiveheights of all protruding members as shown in FIGS. 4A, 4C, 5A, 5B and5C are defined by the high point of any part of the free end (oppositeof base 214 connected end) of the protruding members. This statement isgenerally true irrespective of the design angle Theta 1, Theta 2 andTheta3. The highest and lowest points of protruding members of the group(of quantity three to four) therefore define the rotation angle (Theta1,Theta2, Theta3) of the sealing member (261, 288, 262) as shown in FIGS.4A, 4B and 4C. This submission aims to incorporate the variability ofall designs of protruding members (as seen in FIGS. 4A, 4B and 4C) andthe variability of the general shape of the individual members (ifdesign FIG. 4B design is not utilized) so that the description heir indescribes the defining or significant characteristics of thesecomponents as they relate to the overall functioning of this invention.

FIG. 6 is an enlarged cross-sectional view of the new designincorporating one of the possible sealing members 288 (as shown in FIG.4B) in an assembly which is shown in orientation prior to any contact ormovement of the active components. The sealing member 288 is utilized(from FIG. 4B) and is incorporated in FIG. 6 only for purposes of easeof explanation as its geometry is most simple to display. The view inFIG. 6 is a cross-sectional plane 4-4 taken from FIG. 9 depicting thenew components, including: male coupler 400, female coupler 401, sealingmember 288 and a figurative depiction of both required seals 420 (andoptional stop 430 and lock 430). As shown in FIG. 6, the sealing surface278 (see FIG. 4B) of sealing member 288 is in direct contact withsealing surface 330 (see FIG. 8B). The resultant contact of surfaces 330(one surface of female coupler body 401) and surface 278 (a surface ofsealing member 288) provide the seal between the two components ofsealing member 288 and female coupler body 401. In the orientation ofcomponents as shown in FIG. 6, the fluid pressure that exists within the560 central chamber (cavity) as shown in FIG. 6 is physically containedby surfaces 301, 282, 304 and 330 (between surfaces 330 and 278) and allof the surfaces of the typical hose 202 (tubes, pipes) (as shown in FIG.2). The pressure in central chamber 550 is assumed to be a low valueapproaching atmospheric pressure and is therefore considered negligible.

The resultant pressure in the central chamber 560 (cavity) causesmovement of part 288 (in the direction 905) against part 401 andtherefore, surfaces 330 and surface 278 touch (interfere) and provide aseal. Again, the actual physical design of the seal can utilize avariety of commercially-available options although for simplicity ofexplanation and illustrations, FIGS. 6, 7 and 8 are depicted since theyare the simplest to display (i.e. seals between two simple and compliantsurfaces).

The sealing surfaces are shown in FIG. 7, which is a cross-sectionalview taken along line 7-7 of FIG. 6. This figure shows that the sealingarea (sealing surface only) is defined by the area that is formedbetween: (1) larger circle (dotted) created as the extent of surface 304as projected onto the lip of part 401 which is surface 330, and (2) thesmaller circle defined by the smallest circle shown in FIG. 7 which isthe side view of surface 305. These surfaces 305 and 304 are shown inFIG. 7 as circular which is one of the typical and practical shapes thatthese surfaces may take, although are not limited to only perfectlycircular shapes in concept.

FIGS. 8A, 8B and 8C are sectional views of the invention at variousstages of functioning and male coupler engagement. FIG. 6 displays themale coupler 400 in its pre-contact view. FIG. 8A displays the malecoupler 400 in its initial first contact stage and the direct responsevalve is in its closed position. FIG. 8B shows the male coupler 400 inits highest surface contact and complete rotation of sealing member 288stage; at this stage the direct response valve is at itsinitially-opened position. FIG. 8C displays the male coupler 400 in itsfinal and fully engaged stage of operation; at this stage the valve isin its fully-opened position. In FIG. 8A through FIG. 8C, only the malecoupler 400 and sealing member 288 move in direction 910 and rotation430, while the female coupler 401 remains stationary. [See formerdescription of the opposite form of engagement in which male coupler 400is stationary and female coupler 401 moves in direction 905 and 288moves in direction 905 and also rotates in direction 430. This oppositedirection of movement still provides the same opening of sealing member288 although this movement is not depicted in any figures.

FIG. 8A shows male coupler 400 in its initial first contact stage as themale coupler starts movement in direction 910 along axis 100. Malecoupler 400 makes initial contact with sealing member 288 at the highpoint 251 b of sealing member 288. The male coupler 400 continues tomove in direction 910 along axis 100 past the orientation as shown inFIG. 8A. This causes translation of the sealing member in direction 910and rotation of the sealing member 288 in direction 430 due to theangled surface (Theta 2) of the sealing member 288 (relative to surface340 of part 400). This rotation of part 288 in direction 430 is centredapproximately around a rotation point 402, as detailed in the blow up ofFIG. 8B. Point 402 is located approximately at the outmost edge (topleft hand corner) of part 288 (as orientated in all FIG. 8) in which theouter edge of part 288 (circular line where surfaces 278 and surface 304meet) touches surface 330 as detailed in the blow-up of FIG. 8B. Theexact rotation point is physically dependent on the style of theparticular seal used, although the rotation in direction 430 of sealingmember 288 will generally occur around the same region of point 402. Intypical use, there exists a pressure in the interior cavity 560, whichis created by contained fluid. In turn, this pressure causes a forceonto part 288 as exerted in direction 905 (assuming part 401 isstationary) from application of the internal pressure in centralchambers 560 on surface 282. The force on part 288 in direction 905causes a transfer of force at high point 251d from part 288 to part 400.This contact occurs since part 400 is moving in the direction 910 andpart 288 is moving in the opposite direction 905. This resistance force,which is a result of the insertion of part 400, increases as themovement of part 400 in direction 910 continues. At a specific angle notexplicitly depicted in figures (Theta 12; where Theta 12 is less thanTheta10) the seal breaks and fluid communication occurs between centralchambers 560 and 550. This angle (Theta 12) is entirely dependent on thestyle and materials used in the specific seal design and on the physicalgeometry of the sealing member. Regardless of the seal design that isincorporated, the description heir in remains valid and the fluidcommunication simply starts at a unique and repeatable angle (thespecific angle is unique to seal design and materials chosen which inturn determines the unique Theta 12). Once the seal breaks, theresistance force of insertion reduces due to the flow of fluid out ofcentral chamber 560. Part 288 thus continues to rotate in direction 430until it reaches the orientation shown in FIG. 8B where part 288 hasrotated to its maximum Theta 10 (angle extent) and surface 277 (of part288) is now coincident with surface 340 (of part 400). FIG. 8B alsodemonstrates that the rotation point of part 288, 402, is still incontact with surface 330. Since there remains contact between part 288and part 401 (at the rotation point 402), the force of insertion of part400 from the breaking of seal position to this position remains lessthan all standard and typical existing designs as depicted in FIG. 3.The insertion force required is less than existing designs becausesurface 330 continues to react (resist or supports in direction 910)some of the force exerted on part 288 in direction 905 (from internalpressure within central chamber 560) which results in less insertionforce being required on part 400 in the direction 910.

As shown in FIG. 8B, because part 288 is in direct contact with part400, any further linear movement of part 400 due to continued insertionof 400 in direction 910 results in both parts 400 and 288 now moving intandem in the direction 910 along axis 100. No further rotation of part288 occurs. There continues to be fluid communication between centralchamber 560 and central chamber 550. The desired fluid communicationoccurs from central chamber 560 through the gap (opening betweensurfaces) created between surfaces 330 and 278 subsequently this occursthrough the internal holes 260 which exist in part 288, and out of thecentral chamber of part 288 and finally into central chamber 550. Thiscontinued fluid or gas flow continues to further reduce the resistantforce of insertion of part 400 in direction 910. As depicted in FIG. 8C,depending on the commercially available design utilized for the lockingmechanism 430 (and physical stop 430) the linear motion of parts 400 androtated part 288 in direction 910 (at constant angle Theta 11) ceases.FIG. 8C also displays the final stage of engagement, which is when thephysical stop 430 (and locking mechanism 430) also stop furtherinsertion (resists further motion of 400 in direction 910). The lockingmechanism 430 also typically includes a physical stop 430 and are onlydiscussed since both features are typical in all practicalquick-disconnect assemblies although neither are considered uniquefeatures of this new design. Lock 430 and stop 430 are included fordiscussion only because they do provide convenience to the user.

The sum of the total force (F) of insertion (force on part 400 as it isinserted) through the total distance (d) of travel distance 410 andhence the total work (W), of insertion, required (W=F×d) for this newdesign is considerably less than existing prior-art designs. The exactreduction in force achieved when modifying a particular existing design(modifying old sealing member to the new sealing member design andpossible modifications of associated supporting parts) can easily beconfirmed by lab experiments and/or simulations.

Since the connector insertion force is usually exerted by a human, andsince all humans have maximum physical force limitations and total workoutput limitations, the improvement offered by this invention providesdramatic improvement in consumer usability. This new design isparticularity of benefit in fluid systems which utilize higher pressurefluid or gas levels. High fluid or gas pressure levels exist in mostresidential pressured water systems and in most commercial water, fluidor gas delivery systems.

In this specification have been described, including a number ofparticular mechanical arrangements of the protruding members, sealingmember and seals; it will be understood that other forms, which operatein the same manner as that described, can be readily utilized in thisinvention.

In addition, it is understood that whilst the invented valve isparticularly useful in quick-disconnect assemblies operated by humansthat its benefits are also applicable in uses of automation such asrobots and other automation.

All such modifications and applications are deemed to be within thespirit and scope of the invention.

Any references in this invention to the term “liquid” or “fluid” are tobe analogous and replaceable with any known liquid or gas material whichbehaves as a liquid or gas which includes and is not limited to water,fluids, all liquids, all gases, compressed gases, ngl, cng, Ng, slurriesand gels.

Utilizing a standard cylindrical coordinate system with axial [typical Zdirection], radial [typical Euclidean radial distance from Z axis] andcircumferential [angular] directions; where the axial directioncoincides with the upstream direction 910 and the downstream direction905; the axis of the axial direction is depicted as line 100 on FIGS. 3,6, 8A, 8B and 8C; where the radius [R] has a magnitude of zero at theaxial [Z] axis 100; hence the resulting circumferential directioncoincides with the standard circumferential direction of the coordinatesystem.

What is claimed is:
 1. A sealing member in a quick-disconnect couplerassembly, comprising: a coupler having first and second coupler partswhich are capable of being coupled together when the upstream part isunder fluid pressure, lockable in a coupling position, said couplinghalves comprising a male coupler and a female coupler, lockable in acoupling position; said male coupler and said female coupler couple in atypical linear axial action; said female coupler contains a sealingmember acting as a check valve and biased and held in the closedposition by internal upstream pressure in female coupler; said sealingmember of said female coupler having a stop restricting and definingtotal displacement travel of said male coupler during insertion; saidfemale coupler having a hollow cylindrical body located within thecentral fluid chamber which one annular surface provides a sealingsurface for the said sealing member; said female coupler contains a saidlocking mechanism which is of typical prior-art origin and whosefunction is to lock the said male coupler and the said female couplertogether in the fully engaged coupled position, where the said sealingvalve is in its fully-opened position; a seal member extendingcircumferentially contained within the outer diameter of said malecoupler, proving for a fluid seal between the outer diameter of the saidmale coupler and the inside diameter of the female coupler, to ensurethat fluid does not escape the quick-disconnect coupler and is oftypical prior-art origin and design; a body having an upstream end forreceiving a fluid source and a downstream end for connecting downstreamdevices; said male coupler half contains a hollow cylindrical end whoseradial size(s) correspond with the mating sizes of the said sealingmembers engaging surfaces of varying types and styles and geometricshapes; said male coupler hollow cylindrical downstream end is shaped asto provide a flat plane perpendicular to axial direction; a sealingmember (check valve) with an approximate circular geometry is containedby proximity in a corresponding circular hollow tubular upstream femalecoupler chamber; wherein the sealing element is not physically attachedto any other portion of the upstream or downstream body and is held inits relative location by surface contact between the sealing element andthe relative surfaces of the upstream female coupler body; the sealingmember is of the direct response valve style which is activated and heldin the closed position by the internal upstream pressure within saidinternal chambers of said female coupler; the sealing member containsprotrusions in the downstream direction whose physical orientationcorrespond with the said male coupler cylindrical end, in the radialdirection, during insertion of the two parts; these protrusions interactwith the said male coupler cylindrical end, during part insertion, whichopens the sealing member; the said quick-disconnect assembly containssaid female coupler orientated in the upstream direction and said malecoupler is orientated in a relative downstream direction; upstream isconsidered the supply of fluid direction and hence the above mentionedsealing member must resist fluid flow and resultant fluid pressure fromthe upstream direction.
 2. An improvement to the said sealing member ina quick-disconnect coupler assembly according to claim 1, wherein thesealing member is engaged or opened firstly in a rotational manner andthen secondly, if desired, in a more typical axial translational manner.Following the initial rotational phase, the sealing member is nowtranslated in an axial direction (although remains rotated) whichfurther opens flow channels, improving fluid communication, theimprovements comprising: utilizing a standard cylindrical coordinatesystem with axial [typical Z direction], radial [typical Euclideanradial distance from Z axis] and circumferential [angular] directions;where the axial direction coincides with the upstream direction 910 andthe downstream direction 905; the axis of the axial direction isdepicted as line 100 on FIGS. 3, 6, 8A, 8B and 8C; where the radius [R]has a magnitude of zero at the axial [Z] axis 100; hence the resultingcircumferential direction coincides with the standard circumferentialdirection of the co-ordinate system; a sealing member (check valve) withan approximate circular geometry is contained by proximity in acorresponding circular hollow tubular upstream female coupler chamber;wherein the sealing element is not physically attached to any otherportion of the upstream or downstream body and is held in its relativelocation by surface contact between the sealing element and the relativesurfaces; the sealing member may take various shapes although the saidfemale coupler inner chamber must accommodate the sealing member so thatsealing member is allowed to rotate and translate without restrictionduring all stages; also the physical shape of the sealing member and itssaid female coupler inner chamber surfaces allow the sealing member towithout restriction rotate and translate so that the internal pressurewithin the annual chamber of the female housing continues to thrust thesealing member against the sealing surfaces of the said female coupler;the primary features of the design of the sealing member (valve) bodyare that it must comprise a smaller size than the inside annular cavityof the female coupling body, as it rotates to its maximum rotationposition and, that the sealing members axial sealing surface mustclosely match, in a circumferential manner the same or similar axialshape of surfaces as the matching female coupling; a sealing memberwhich acts as one solid body in functionality and may be manufactured ofvarious materials, components and parts whose individual components orparts are finally assembled to act as one solid body that in itsentirety (whole) behaves in the manner as described heir in; a sealingmember is movably mounted in the female coupler housing to moverotationally between the closed position and the initially-openedposition. In the closed position the sealing member is aligned axiallyrelative to the female housing and in the initially-opened position, thesealing member is rotated (perpendicular to the axial direction)relative to the female and male housings; a sealing member whose sealingsurface plane is generally defined at a fixed axial location and thepure radial direction; the said ends of said cylindrical column of saidmale coupler axial ends define a plane which generally is coincidentwith the above mentioned sealing surface plane; the two above mentionedplanes are at the same angle perpendicular to the axial direction; sincethese two above mentioned planes are generally coincident these twoplanes are used interchangeably within; a sealing member which containsa sealing surface located on the upstream side of the sealing member; asealing member with a downstream surface, comprised of protrusions ofvarying shapes and sizes whereas the axial ends of said protrusionsdefine an angled plane, relative to the pure radial direction(perpendicular to the axial direction), which contact the said ends ofsaid cylindrical column of said male coupler during insertion of thesaid male coupler into said female coupler; said protrusions, since theydefine a said plane which is not coincident with the said plane definedby the said ends of the said cylindrical column of said male coupler,serve to ensure that the sealing member firstly rotates (perpendicularto the axial direction) during the valve opening sequence; the rotationoccurs around the contact of the axial high point of the said protrudingsurface and the corresponding radial location of the said axial ends ofsaid cylindrical column of said male coupler during insertion of thesaid male coupler into said female coupler; the said described rotationceases when the lowest axial point, defining the protrusion planedescribed heir in, contacts the corresponding radial location of thesaid axial ends of said cylindrical column of said male coupler duringinsertion of the said male coupler into said female coupler; the maximumtranslation of the already-rotated sealing member in an axialtranslation direction is limited by the said stops and the lockingmechanism utilized which will stop further insertion of the malecoupler; this submission asserts that whilst the invented valve isparticularly useful in quick-disconnect assemblies operated by humansthat its benefits are also applicable in uses of automation such asrobots and other automation; in this specification have been described,including a number of particular mechanical arrangements of theprotruding members, sealing member and seals; it is claimed that otherforms, which operate in the same manner as that described, can bereadily utilized by this invention; an improvement whereas the method bywhich the direct response valve member is opened substantially reducesthe force required to open the direct response valve, as compared toprior-art designs; an improvement whereas the sum of the work (Force xDistance) done between the closed position and the fully-opened positionis far less than prior-art designs; this improvement is applicable toquick-disconnect couplers which transport any liquid, fluid, gas or anyproduct which behaves as a liquid or gas; which includes and is notlimited to water, fluids, all liquids, all gases, compressed gases, ngl,cng, ng, slurries and gels; any modifications and applications, whichoperate in the same manner as that described heir in, are deemed to bewithin the spirit and scope of this invention.
 3. The improvement asdefined in claim 2 wherein said sealing member is comprised of saidprotrusions whose function is to define a distinct and intentional anglebetween the sealing members sealing surface and the surface of thesealing member containing the protrusions; heir in the angle of a planeis defined as its angular position perpendicular to the axial axis;although not mandatory, typically the sealing surfaces on the femalebody are located on a plane with constant axial locations; the sealingsurface is located in upstream direction on the sealing member and theprotrusions are located in the downstream direction on the sealingmember; these said protrusions may consist of various quantities andshapes and still serve the primary function of providing a plane that isnot coincident with the sealing members sealing surface plane; thisclaim asserts that the protrusions can be of the following geometry, orconsist of other geometry not defined heir in, and still meet therequirements of defining a plane which will cause the required movementof the sealing member as follows: three distinct and separate saidprotrusions; the three collective ends of three protruding surfaces (asystem) define a flat plane that is at a distinct angle relative to thesaid sealing surface; a design may also incorporate more than threeprotruding surfaces (protrusions) although no design considerationsincluding more than three protruding surfaces provide any practicaladvantages since a surface can be uniquely defined by the location ofonly three points in space (three said protrusions or more); theindividual protruding members may take any desired practical shape, asdetailed within this submission, whereas the ends of the saidprotrusions that contact the male coupler said mating surfaces definethe plane and the remaining inactive parts of the said protrudingmembers shapes and surfaces are immaterial, as long as these surfaces donot interfere with the rotational and axial displacement of the sealingmembers movements; a singular protruding cylindrical shape (hollowtruncated cone) is a cylindrical protrusion that, by its nature, doesnot have distinct and separable protrusions; the option of theprotruding member shape must incorporate holes of any desired shapewhich provide a fluid path between the inner cylindrical and outercylindrical surface of this protruding member and are sufficient intotal area to allow desired fluid flow quantities; these said holes arerequired, since the shape is cylindrical and by its nature thiscylindrical shape will prevent fluid flow without any holes; the highestand lowest points of any two protruding members of the group (a quantityof two or more), relative to the base of attachment of the protrudingmembers, therefore define the maximum distance at a set radial distanceapart and hence define the maximum rotation of the sealing member duringfull engagement; this submission asserts that this angle is a designconsideration that would be chosen by detailed design and would considerrequirements including: the fluids properties, pressure losses and flowrequirements; the said angle is intentionally not defined as a finitenumber since it is a chosen design parameter based on the abovementioned; the heir in described rotation of the sealing member resultsin increased fluid communication between the internal chambers of themale coupler and female coupler; any modifications and applications,which operate in the same manner as that described heir in, are deemedto be within the spirit and scope of this invention.
 4. The improvementas defined in claim 2 wherein said sealing member is movably mounted inthe female couplers housing in order to move rotationally between theclosed position and the initially-opened position. In the closedposition, the sealing member is aligned axially relative to the femalehousing and in the initially-opened position, the sealing member isrotated relative to the female and male housings as follows: the saidmale coupler whose cylindrical end first contacts the said highestprotrusion point end; the sealing member is not restricted in thecircumferential direction which allows the sealing member to rotatecircumferentially; hence the actual rotation point on the said sealingsurface of the female coupler could effectively be at any point in acircle on this sealing surface; the ability of the sealing member torotate circumferentially is a characteristic of the design, and whilenot a benefiting attribute, does differentiate this design; the sealingmember rotates perpendicular to the axial coordinate due to theresultant moment (force×distance) since the one-point contact is notsymmetrical to the axial centre line of the said quick-disconnect orbody comprised of two halves; as previously described heir in; continuedsaid insertion acts to further rotate the sealing member; dependent onmaterials and seals utilized, the seal between the sealing member andthe said seal on the female coupler body opens, thus starting fluidcommunication between the female coupler and male coupler centralchambers; continued said insertion rotates the sealing member furtheruntil the sealing member rotates to its maximum allowable angledetermined by all active protruding elements (those which define theplane) contained in this design; this continued rotation allows moresaid fluid communication to occur and is defined as the initially-openedposition; In the closed position the sealing member is aligned axiallyrelative to the female housing and in the initially-opened position, thesealing member is rotated relative to the female and male housings; animprovement whereas the method by which the direct response valve memberis opened substantially reduces the force required to open the directresponse valve, as compared to prior-art designs; an improvement whereasthe sum of the work (Force×Distance) done between the closed-positionand this initially-opened position is far less than prior-art designs;any modifications and applications, which operate in the same manner asthat described heir in, are deemed to be within the spirit and scope ofthis invention; since the connector insertion force is usually exertedby a human, and since all humans have maximum physical force limitationsand total work output limitations, the improvement offered by thisinvention provides dramatic improvement in consumer usability.
 5. Theimprovement as defined in claim 2 wherein the already rotated sealingmember is further translated in an axial direction and manner by furtherinsertion of the male coupler. This axial translation results in furtherincreased fluid communication between the internal chambers of the maleand female housings; male coupler end is further inserted into femalecoupler end, until the said stop is reached, which produces thefollowing movement from the initially-opened position to thefully-opened position as follows: an improvement where the said malecoupler cylindrical end and the said sealing member protrusions remainin full contact; and the presently fully rotated sealing membertranslates in a purely axial direction, further improving fluidcommunication between the internal chambers of the male and femalehousings; further axial translation occurs, which results in improvedsaid fluid communication, until the male coupler end contacts the saidstop; the said stop can be incorporated within the mechanism of the saidlatch which holds the said male coupler and female coupler together inthe fully-opened position; this final position of the sealing member isdefined as the fully-opened position; for a given force applied betweenthe closed and fully-opened positions the velocity of the male coupler[and all attached mass] will be higher than prior-art designs since theresistance (required effort) is less; any modifications andapplications, which operate in the same manner as that described heirin, are deemed to be within the spirit and scope of this invention; animprovement whereas the method by which the direct response valve memberis opened substantially reduces the force required to open the directresponse valve, as compared to prior-art designs; an improvement whereasthe force (effort) required, between the closed position and thisfully-opened position is far less than prior-art designs; an improvementwhereas the sum of the work (Force×Distance) done between theclosed-position and this fully-opened position is far less thanprior-art designs; since the connector insertion force is usuallyexerted by a human, and since all humans have maximum physical forcelimitations and total work output limitations, the improvement offeredby this invention provides dramatic improvement in consumer usability.